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WO2018174994A1 - Procédé et système de transfert, de transport et/ou de stockage d'énergie chaude et/ou froide - Google Patents

Procédé et système de transfert, de transport et/ou de stockage d'énergie chaude et/ou froide Download PDF

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Publication number
WO2018174994A1
WO2018174994A1 PCT/US2018/015820 US2018015820W WO2018174994A1 WO 2018174994 A1 WO2018174994 A1 WO 2018174994A1 US 2018015820 W US2018015820 W US 2018015820W WO 2018174994 A1 WO2018174994 A1 WO 2018174994A1
Authority
WO
WIPO (PCT)
Prior art keywords
fine particles
carrier gas
hopper
temperature
media
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/US2018/015820
Other languages
English (en)
Inventor
Hamid Abbasi
David Cygan
S. B. Reddy Karri
John Findlay
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GTI Energy
Original Assignee
Gas Technology Institute
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gas Technology Institute filed Critical Gas Technology Institute
Publication of WO2018174994A1 publication Critical patent/WO2018174994A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S60/00—Arrangements for storing heat collected by solar heat collectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S80/00—Details, accessories or component parts of solar heat collectors not provided for in groups F24S10/00-F24S70/00
    • F24S80/20—Working fluids specially adapted for solar heat collectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D13/00—Heat-exchange apparatus using a fluidised bed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/0056—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using solid heat storage material
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/023—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat the latent heat storage material being enclosed in granular particles or dispersed in a porous, fibrous or cellular structure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/028—Control arrangements therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0004—Particular heat storage apparatus
    • F28D2020/0021—Particular heat storage apparatus the heat storage material being enclosed in loose or stacked elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D2020/0065—Details, e.g. particular heat storage tanks, auxiliary members within tanks
    • F28D2020/0082—Multiple tanks arrangements, e.g. adjacent tanks, tank in tank
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • This invention relates generally to thermal conveyance and, more particularly, to a system and process for absorbing, transporting, storing and/or recovery of thermal energy (defined as both hot and cold energy) over a wide range of temperatures, ranging from subzero to as high as 2,100° F or higher, for heating, cooling and power generation applications.
  • thermal energy defined as both hot and cold energy
  • thermal energy storage A number of specific approaches have been investigated for thermal energy storage.
  • One approach is to hold heat, such as from generated steam, in a bed of sand or refractory material by incorporating embedded steam pipes and to recover the heat later from the hot bed to generate power.
  • a second approach is to transfer the heat to an organic liquid that is then held in a 'hot' tank until needed to generate steam such as for a turbine. After transferring heat, the organic liquid is pumped to a 'cold' tank in preparation for collecting more heat.
  • Organic liquids in such applications are generally limited to operating temperatures well below 750° F, and suffer from problems with volatilization and degradation reactions.
  • Molten salt is pumped through the heat source and collects heat. Then the hot molten salt serves as a heat sink to generate steam at a later time.
  • Molten salts avoid the volatility problems of liquid organic energy storage fluids, and molten salts can work at higher maximum temperatures. This elegance comes with limitations imposed by the properties of the molten salts. The limitations include:
  • Viscosities must be kept low. Over the temperature range of 480-930° F, molten salt mixture viscosities can vary by a factor of 5. This increases pump duty, the cost of pumps, and the electricity needed to pump the molten salts.
  • Nitrate salts can react with carbon dioxide and oxygen in the air to produce carbonate and nitride salts that change the molten salt mixture properties. Even more damaging is the formation of nitric acid by reaction with air at high temperatures.
  • Some molten salt mixtures are expensive. Improving molten salt properties by lowering the melting point, lowering viscosity, increasing working temperature range, and raising temperature can be accomplished by adding other salts such as lithium and calcium nitrate to the mixture. These other salts, especially lithium nitrate, are costly and add significant capital cost to the thermal energy storage system.
  • Molten salts are typically corrosive. Materials for tanks and lines must be carefully selected to limit corrosion. Increasing temperature from 480-930° F can increase corrosion rates by a factor of 4. Compensating for the effects of corrosion adds capital cost. f. The maximum working temperature is undesirably too low. Molten salt mixtures have a maximum working temperature in the range of 750-1020° F. Above this temperature, they suffer from excessive corrosion rates and high levels of side reactions. g.
  • researchers are pursuing the use of single tank nitrate salt storage using tanks with controlled temperature gradients. This approach eliminates one large tank but leads to some increase in size for the single tank and increased complexity and controls.
  • Metals and eutectic metals have generally been less explored as PCMs as compared to organic compounds and salt hydrates. Metals face serious engineering challenges because of their weight. Metals have low heats of fusion by weight but high heats of fusion by volume. Metals have high thermal conductivities and low vapor pressures in the liquid state. Severe penalties for metals are their high weights and their high costs compared with organic compounds (especially paraffins) and salts. As a result, metals and eutectic metals are generally not seriously considered currently as PCMs.
  • thermochemical storage A third major area of energy storage research being actively pursued is thermochemical storage.
  • the range of possible applications for the purpose of heat storage using thermochemical reactions is very wide, however these systems are expected to be more complex and also dependent on reaction rates.
  • ammonia dissociation at 750-1290° F, up to around 2000° F for solar thermal processes in tower plants.
  • There are different possible mechanisms to store enthalpy including:
  • Heat of dilution Adding or removing water to a salt solution
  • a general objective of the subject development is to provide improved processes and systems for absorbing, transporting, storing, and recovering thermal energy (defined as both hot and cold energy) over a wide range of temperatures, from subzero to as high as 2,100° F or higher, for heating, cooling, and power generation applications.
  • thermal energy defined as both hot and cold energy
  • a more specific objective of the subject development is to overcome one or more of the problems described above.
  • a system for operating the process may include a particle storage hopper that holds the fine particles at a hopper pressure (P4) and a hopper temperature (Tl ).
  • the fine particles are preferably selected to have suitable characteristics including, but not limited to, suitable service temperature, melting point, thermal characteristics, radiation characteristics, mechanical characteristics, and flow properties.
  • the fine particles may be selected from carbon, plastic, sand, minerals, refractory, metals, composites, glass and other types of materials.
  • the fine particles have a mean diameter ranging from 10 microns to 1000 microns.
  • the fine particles comprise a mean diameter ranging from 50 to 300 micron.
  • the particle storage hopper preferably connects to a carrier gas source providing a carrier gas at an initial gas pressure (P I ) and an initial temperature (T8).
  • the carrier gas is preferably non-reactive with the fine particles and is preferably selected from the group consisting of air, nitrogen, carbon dioxide, inert gases and combinations thereof.
  • the fine particles from the particle storage hopper combine in a pipeline with the carrier gas to create a two phase thermal media at a media temperature (T2).
  • the two phase thermal media provides a thermal energy fluid for absorbing, transporting, storing and recovering thermal energy over a wide range of temperatures from subzero to 2, 100° F or higher for heating, cooling, and power generation applications.
  • the two phase thermal media enters a heat exchanger with a thermal energy source or sink.
  • the two phase thermal media is then heated or cooled to a heat exchanger output temperature (T3) through transfer of thermal energy between the energy source or sink, respectively, and the two phase thermal media.
  • the two phase thermal media now heated or cooled, passes out of the heat exchanger and flows in a pipeline to a second particle storage hopper where the fine particles are separated from the carrier gas and the fine particles are maintained in the second particle storage hopper at a second hopper pressure (P2).
  • the carrier gas, separated from the fine particles may then be provided to a separator/filter to extract any entrained fine particles remaining in the carrier gas.
  • the heated or cooled fine particles may be stored in the second particle storage hopper until the thermal energy needs to be exchanged.
  • the fine particles maintained in the second particle storage hopper may then be transported and/or used as a thermal energy source or sink to heat or cool.
  • the particle storage hopper When exchanging the hot or cold thermal energy from the fine particles, the particle storage hopper preferably connects to a second carrier gas source that provides a second carrier gas at an initial gas pressure (P3) and an initial temperature (T7).
  • the second carrier gas is preferably non-reactive with the fine particles and preferably may be selected from the group consisting of air, nitrogen, carbon dioxide, inert gases and combinations thereof.
  • the second carrier gas may be the same type of gas as the carrier gas, however it may also be another type of carrier fluid.
  • the fine particles from the second particle storage hopper combine with the second carrier gas to create a second two phase thermal media at a media temperature (T5).
  • the second two phase thermal media is then provided to a second heat exchanger with a second heat source or sink.
  • the second two phase thermal media is then heated or cooled to a second heat exchanger output temperature (T6) through transfer of thermal energy between the second heat source or sink and the second two phase thermal media.
  • T6 second heat exchanger output temperature
  • the heat source or sink is heated or cooled to a desired temperature.
  • Costs can be controlled through choice of materials.
  • Advantages over molten salts include less sensitivity of viscosity to temperature, no need to maintain temperatures above melting point to avoid solidification/freezing, no side reactions, noncorrosive, and potential for much higher temperatures.
  • thermal oils include more efficient storage, no need to maintain temperatures above a certain limit to maintain flow properties, and ability to create a non-flammable gas-particle mixture and ability to operate at low pressures.
  • Figure 1 is a simplified flow diagram illustrating one embodiment of a system for absorbing, transporting, storing and/or recovering thermal energy (defined as both hot and cold energy).
  • FIG. 2 is a simplified flow diagram illustrating one embodiment of a system for collecting solar energy and using the solar energy to generate hot air.
  • a system 10 and process for absorbing, transporting, storing and recovering thermal energy (defined as both hot and cold).
  • the process involves at least one of transferring thermal energy to a thermal energy fluid, storing the thermal energy for at least a temporary period of time, and/or recovering the thermal energy, wherein the thermal energy fluid comprises a two phase thermal media including a gaseous carrier containing a quantity of micron to millimeter sized solid particles and wherein the temperature varies over a wide range of from subzero to as high as 2, 100° F or higher, for heating, cooling and power generation applications.
  • suitable thermal energy fluids comprise a two phase thermal media having fine particles with suitable characteristics mixed with a gas that is non-reactive to the specific particles or particle mixtures.
  • the particle laden two phase thermal media of this invention allows for operation over the working temperature of the solid particles and the working temperatures and pressures of the gas while also providing an increase in the specific heat or cold capacity and heat transfer coefficient of the carrying gas.
  • the fine particles should be selected based on the particle's service temperature, melting point, thermal conductivity, specific heat capacity and absorptivity, and flow and mechanical properties.
  • the fine particles may comprise a single material or a mixture of different materials.
  • the particles may also include phase change materials or encapsulated phase change materials.
  • phase change materials or encapsulated phase change materials.
  • suitable materials can include corundum, silicon carbide, alumina, silica sand, carbon, graphite, graphene, talc, iron, iron oxide, minerals, plastic, refractory material, metals, metal oxides, alloys, composites, glass, and combinations thereof.
  • the fine particles have a mean diameter ranging from 10 microns to 1000 microns. In a preferred embodiment, the particle size ranges from 50 to 300 micron. However, it should be understood that the concept of this invention can be used with a wide range of particle diameters, ranging from submicron to millimeter, by employing appropriate transport and storage systems.
  • the carrier gas preferably does not react with the particles at the prevailing temperatures.
  • gaseous fluids are useable as the carrier gas. Suitable gaseous carriers can include air, nitrogen, carbon dioxide, inert gases and combinations thereof. In accordance with one embodiment, air is a preferred carrier fluid such as for use in an open loop, for example.
  • the two phase thermal media can be used to transfer and store thermal energy from subzero temperatures to at up to 2,100 °F or higher depending on the process needs and hot/cold source availability.
  • Figure 1 is a simplified (low diagram illustrating one embodiment of the system 10.
  • the system 10 includes two particle storage hoppers 12, 14 along with two heat exchangers 16, 18.
  • the system 10 shown in Figure 1 is an example of the system of this invention.
  • the invention can comprise a wide variety of different arrangements with additional hoppers, filters, valves etc. for continuous or intermittent heat (or cold) storage and continuous or on demand recovery of heat (or cold).
  • the system 10 may also include either a single hopper and/or a single heat exchanger.
  • fine particles held in the first particle storage hopper 12 at a temperature Tl are mixed with a compressed carrier gas at pressure PI and temperature T8, forming a two phase thermal media at temperature T2.
  • the two phase thermal media flows via a line 24 to the first heat exchanger 16.
  • the two phase thermal media is heated (or cooled) to temperature T3 through transfer of thermal energy between the two phase thermal media and the heat (or cold) source.
  • the two phase thermal media, at temperature T3, then flows via a line 26 to the second particle storage hopper 14 where it is maintained at pressure P2, and the heated (or cooled) fine particles are separated from the carrier gas and disengaged in the hopper 14.
  • the pressure P2 is lower than the pressure PI .
  • the carrier gas together with any entrained fine particles exits the second particle storage hopper 14 and flows to a separator 20 and/or a filter 22 (cyclone, ceramic filter etc. or combination) to capture the particles for collection and discarding or for recycling back into the flow loop.
  • the fine particles held in the second particle storage hopper 14 at temperature T4 are mixed with a second compressed carrier gas at a pressure P3 and a temperature T7, forming a second two phase thermal media, at a temperature T5.
  • the second two phase thermal media then flows through a line 28 to the second heat exchanger 18.
  • the second two phase thermal media is heated (or cooled) to temperature T6 through transfer of thermal energy between the second two phase thermal media and the heat (or cold) product fluid.
  • the cooled (or heated) second two phase thermal media then flows through line 30 back to the first particle storage hopper 12, maintained at pressure P4, where the fine particles are separated from the second carrier gas and disengaged in the first particle storage hopper 12.
  • pressure P4 is preferably lower than the pressure P3.
  • the carrier gas with entrained fine particles exits the first particle storage hopper 12 and flows to the separator20 and/or the filter 22 (cyclone, ceramic filter etc. or combination) to capture the particles for discarding or for recycling back into the flow loop.
  • FIG. 2 is a simplified flow diagram illustrating an embodiment of the invention for collecting solar thermal energy and using it to generate hot air, generally designated by reference number 100.
  • the system 100 includes a cold particle storage hopper system 102, a hot particle storage hopper system 104, a solar collector bank 106, a heat exchanger 108, a first carrier gas supply 1 10 and a second carrier gas supply 1 12.
  • each of the subsystems is connected by a plurality of lines and valves.
  • the invention can comprise a wide variety of different arrangements with additional subsystems, filters, valves etc. for continuous or intermittent heat (or cold) storage and continuous or on demand recovery of heat (or cold).
  • the cold storage hopper system 102 includes a cold storage hopper 1 14, a cold surge hopper 1 16 and a cold lock hopper 1 18.
  • the cold storage hopper 1 14, the cold surge hopper 1 16 and the cold lock hopper 1 18 are preferably connected through a series of lines and/or valves to provide a supply of the fine particles at a desired hopper temperature and/or hopper pressure.
  • the cold storage hopper system 102 connects to the first gas supply 1 10 via a line 120, where the fine particles mix with a compressed carrier gas from the first gas supply to form a two phase thermal media at a media temperature and a media pressure.
  • the two phase thermal media is then provided to the solar collector bank 106.
  • the solar collector bank 106 heats the two phase thermal media to a solar collector bank output temperature through transfer of thermal energy from the solar energy source to the two phase thermal media.
  • an output line 122 from the heat exchanger allows the two phase thermal media to flow to the hot particle storage hopper system 104 comprising a hot storage hopper 124, a blow tank 126 and a hot lock hopper 128, where the fine particles are separated from the carrier gas.
  • the fine particles are maintained in the second particle storage hopper system 104 at a second hopper temperature and a second hopper pressure.
  • the heated fine particles are held in the hot particle storage hopper system 104 until needed.
  • the hot storage hopper system 104 connects to the second carrier gas supply 1 12 via a line 130, where the heated fine particles mix with a compressed carrier gas from the second carrier gas supply to form a second two phase thermal media at a second media temperature and a second media pressure.
  • the second two phase thermal media is then provided to a system for a desired purpose including heating and/or power generation applications.
  • the second two phase media passes to the heat exchanger 108.
  • the heat exchanger includes a product fluid.
  • the second two phase thermal media transfers thermal energy to the product fluid.
  • the heated product fluid is then provided to a system for a desired purpose including heating and/or power generation applications.
  • the second two phase thermal media then preferably passes through a line 132 and back to the cold particle storage hopper system 102.
  • the system 100 can be used with the fine particles stored or continuously circulated through the system as needed.
  • an operating procedure of the system 100 involving 6-hours of storage might include the following steps:
  • the cold storage hopper 1 14 is provided with at least a 6-hour supply of the fine particles and pressurized at an initial hopper pressure, and the hot storage hopper 124 is initially empty and depressurized.
  • the fine particles, at an initial cold temperature are combined with the first carrier gas forming the two phase thermal media.
  • the two phase thermal media is the provided to the solar collector bank 106 at a flow rate Wl .
  • the solar collector bank 106 the two phase thermal media is heated via thermal energy transfer with the solar energy source.
  • the heated two phase thermal media then flows to the hot storage hopper system 104 at the rate Wl , where the heated fine particles are separated from the carrier gas.
  • the heated fine particles are then combined with the second carrier gas, forming the second two phase thermal media that flows to generators from the blow tank 126 at rate W2, where the rate W2 is less than the rate Wl .
  • the cooled second two phase thermal media preferably flows back to the surge hopper 1 16 at the rate W2.
  • the hot lock hopper 128 is filled and valves switch allowing the heated two phase thermal media to flow to the hot storage hopper 124 and the hot lock hopper 128 is pressurized. The solid fine particles are then transferred from the hot lock hopper 128 to the blow tank 126 to maintain a flow of the solid fine particles to the generators.
  • the hot lock hopper 128 is empty, the hot lock hopper 128 is depressurized, and the valves switch to allow the fine particles to flow back to the hot lock hopper 128 from the hot storage hopper 124.
  • the valves are switched to direct the fine particles to the cold lock hopper 1 18.
  • the cold lock hopper 1 18 is full, the cold lock hopper 1 18 is pressurized, and flow to the energy source is switched from the cold storage hopper 1 12 to the cold lock hopper 1 18 and maintained at rate Wl .
  • the cold lock hopper 1 18 is empty, solids flow Wl is transferred back to the cold storage hopper 1 12, the cold lock hopper 1 18 is depressurized, and refilled from the surge hopper 1 16.
  • the embodiments described in this application are merely exemplary, a wide range of other configurations of this invention are possible.
  • the invention of this application can be used to transport, store and recover both heat and cold energy from a variety of sources over a wide range of temperatures.
  • the development herein described can, if desired, be used or employed in a continuous heating-cooling configuration such as where both heating and cooling are carried out continuously and simultaneously.
  • the subject development can be used or employed without one of the hot and cold storage vessels or in a closed loop such as using an in line particle-gas mixture pump. Further yet, at least a portion of the carrier gases can be recovered for reuse.
  • the invention may include suction pumps on the exhaust of the hoppers to pull the two phase thermal media into the loop.
  • both pressurized carrier gas and exhaust suction pumps can be employed to promote circulation and flow.
  • the clean exhaust gas separated from the fine particles, after the cyclone separator and/or filter package can be recycled back and used as the carrier fluid in a mostly closed loop arrangement.
  • a portion of the carrier gas may be injected into at least one of the hoppers, at least intermittently, to promote particle fluidization and mixing of stored particles. It is to be understood and appreciated that transport and/or storage systems employed in the practice of the processing herein described can be operated under pressure or under vacuum, as may be desired for particular applications.
  • heat transfer between the particle- gas mixture and the heat or cold source or sink could be by various means, including radiation or direct contact between particles and the heat or cold source or sink.
  • filtering and/or feeding component(s) can suitably be incorporated and, if desired, integrated such as with or in a storage vessel or built into a separate housing and connected to the vessel, such as may be desired for particular applications.
  • a preferred approach is to use or employ a dense phase transport, e.g., a dense phase loading of the micron to millimeter sized solid particles, to maximize heat transfer rates and minimize transport velocity, particle attrition and transport component erosion.
  • suitable flow loop designs can incorporate single or multiple branches separating and combining as appropriate, and one or more storage vessels can be used for either or both cold and hot storage of particles.
  • the heat and/or cold energy source and/or sink may comprise a single source or multiple sources.
  • thermally insulated transport and storage components may be preferred to reduce or minimize thermal losses, for example, hot media becoming cooler during transport and/or storage or cold media becoming warmer during transport and/or storage.
  • the concept of this invention is applicable to a wide range of processes that have excess heat or cold energy that can be captured and used at a different location and/or a different time. It allows the storage and on-demand use of cold and heat energy.
  • hot energy sources are solar energy, thermal energy in the exhaust gases of continuous and batch type industrial furnaces, exhaust gases of fired equipment and energy in flares, but the concept can capture and transport as well as store and recover cold and heat energy from a wide range of sources.
  • cold energy sources are ice, nighttime cooler air and chilled water.

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  • Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Chemical & Material Sciences (AREA)
  • Sustainable Energy (AREA)
  • Combustion & Propulsion (AREA)
  • Sustainable Development (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)

Abstract

L'invention concerne un système de transport thermique et un procédé d'absorption, de transport, de stockage et de récupération d'énergie thermique (à la fois de l'énergie chaude et de l'énergie froide) sur une large plage de températures allant jusqu'à 1150 °C (2100 °F), ou plus, ou une énergie froide à des températures inférieures à zéro dans des particules inertes et stables sans qu'il soit nécessaire de maintenir une température minimale ou nécessitant des pressions de système élevées. Le processus implique le transfert d'énergie thermique vers un premier fluide de transfert et la récupération d'énergie thermique à partir d'un deuxième fluide de transfert, les premier et deuxième fluides de transfert comprenant un milieu thermique à deux phases comprenant un support gazeux qui contient une quantité de particules solides de taille micrométrique à millimétrique.
PCT/US2018/015820 2017-03-20 2018-01-30 Procédé et système de transfert, de transport et/ou de stockage d'énergie chaude et/ou froide Ceased WO2018174994A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US15/463,333 US11255575B2 (en) 2017-03-20 2017-03-20 Process and system for hot and/or cold energy transfer, transport and/or storage
US15/463,333 2017-03-20

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WO2018174994A1 true WO2018174994A1 (fr) 2018-09-27

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BR112021005563A2 (pt) 2018-09-24 2021-06-29 Alliance For Sustainable Energy, Llc sistemas de armazenamento de energia térmica baseados em partículas
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